Reversing feed gear shaping machine



June 2, 1953 E. w. MILLER REVERSING FEED GEAR SHAPING MACHINE l0 Sheets-Sheet 1 Filed Aug. 2, 1945 Fav maria/{afar H "1 iL.

E. W- MILLER REVERSING FEED GEAR SHAPING MACHINE June 2, 1953 10 Sheets-Sheet 2 Filed Aug. 2, 1945 I I l J r I Jdwara 2417/3 22?? l l l l l l I I l IL E. W. MILLER REVERSING FEED GEAR SHAPING MACHINE June 2 1953 10 Sheets-Sheet 3 Filed Aug. 2, 1945 June 2, 1953 E. w. MILLER REVERSING FEED GEAR SHAPING MACHINE 1O SheetsSheet 4 Filed Aug. 2, 1945 I E. w. MILLER REVERSING FEED GEAR SHAPING MACHINE June 2, 1953 10 Sheets-Sheet 5 Filed Aug. 2, 1945 .June 2, 1953 E. w. MILL ER REVERSING FEED GEAR SHAPING MACHINE Filed Aug. 2, 1945 10 Sheets-Sheet 7 aw/A5255 A ill.

ll 2.5:: I- II I 15 067827 & 412M7 5 filifiw 3 June 2, 1953 E. w. MILLER REVERSING FEED GEAR SHAPING MACHINE l0 Sheets-Sheet 8 Filed Aug. 2, 1945 jiwari W June 2, 1953 w, MILLER 2,640,397

REVERSING FEED GEAR SHAPING MACHINE Filed Aug. 2, 1945 10 Sheets-Sheet 9 L if 15 June 1953 E. W. MILLER 2,640,397

REVERSING FEED GEAR SHAPING MACHINE Filed Aug. 2, 1945 10 Sheets-Sheet l0 5 I I Z520e7%7 Jdzuawd Zd Patented June 2 1953 REVERSING FEED GEAR SHAPING MACHINE Edward W. Miller, Springfield, Vt., assignor to The Fellows Gear Shaper Company, Springfield, Vt., a corporation of Vermont Application August 2, 1945, Serial No. 608,415

9 Claims.

The present invention relates to the art of generating and cutting gears by the use of a planing cutter having teeth similar to gear teeth but formed with cutting edges on one end and side clearance back from the cutting edges. The cutters referred to are the well known Fellows gear shaper cutters, illustrations of which are given in the patent of E. R. Fellows No. 676,226, June 11, 1901. The main object of the invention is to increase the life of the cutter by equalizing the wear on both side edges and the tip edge of the cutter teeth.

Heretofore in the practice of generatin gears by reciprocation of a gear shaper cutter and simultaneous rotation of the cutter and work, the cutter has been rotated always in the same direction when cutting a number of gears in succession, and all of the gear blanks have been rotated in the same direction, which is opposite to the rotation of the cutter when external gears are generated, and the same as that of the cutter when generatin internal gears. This has resulted in the cutting edges at the advancing side of the cutter teeth being subjected to much more severe duty and wear than the trailing edges and becoming so dull as to require resharpening while the trailing edges are still sharp enough to perform satisfactory cutting action. Sharpening is effected by grinding away the end faces of the cutter teeth and adjacent end surface of the cutter. When repeated rindings have shortened the teeth to the point where they are not strong enough to be depended on, the useful life of a cutter is ended.

The present invention comprises the method of equalizing wear on both side edges of the cutter teeth by reversing the direction of its rotation, and that of the spindle which carries the work gears, from time to time, so that the opposite side edges become alternately the leading edges; and timing the reversals with respect to the cutting action in such manner that substantially or nearly equal numbers of cutting strokes are made while rotation in each direction is going on. Preferably such reversals are effected at the commencement of the cutting action on each new blank work piece, and certain features of the machine are correlated with the procedure of so doing. However, in the broad aspects of the invention, reversals may be made at other intervals, for instance after two or more gears have been cut.

The invention further comprises novel combinations and organizations in gear shaping machines by which reversals of cutter and work spindle rotations are effected at the prescribed times. It comprises, still further, automatic reversing means for controlling the direction of back off between the cutter and work to avoid rubbing contact during the non cutting strokes.

In some cases, depending on the number and form of the cutter teeth and the dimensions of the gear blank, interference occurs between the cutter teeth and work at one or more points when the backing off movement takes place on the line of centers of cutter and work piece, and in such cases the direction of back off is inclined at a suitable small angle to the line of centers; wherefore, when the direction of rotation is reversed, the back 01f path must be inclined at an opposite, and generally an equal, angle to the line of centers, as otherwise the interference difficulty would be intensified. The invention also includes means for effecting reversal of the drive for the depth feeding means relative to the cutter rotation, when that rotation is reversed, in those machines which are equipped with depth feeding means and in which the invention is embodied.

A machine effective for accomplishin the objects and containing the principles stated and implied in the foregoing introduction, and constituting one illustrative embodiment of the invention, is described in the following specification, and shown in the accompanying drawings, in which,

Fig. 1 is a front elevation of the machine with parts broken away and. shown in section;

Fig. 2 is a vertical cross section on line 22 of Fig. 1, as seen from the right hand side;

Fig. 3 is a vertical cross section taken on line 3-3 of Fig. 1, looking in the direction of the arrows on that line;

Fig. 4 is a horizontal section taken on line A@ of Figs. 1, 2 and 3;

Fig. 5 is a section taken on line 55 of Fig. 4 showing a detail of mechanism;

Fig. 6 is an elevation of the mechanism shown in Fig. 5, as seen from the line 6-6 of the latter figure;

Fig. 7 is a substantially vertical section taken on line 1-7 of Fig. 3;

Fig. 8 is a view shown in front elevation of the parts in rear of the line 8-8 on Fig. 3;

Fig. 9 is a detail sectional view of the reversible gearing shown in Fig. 7, taken on the plane which includes the axes of the several gears;

Fig. 10 is a horizontal section taken on line Ill-l0 of Figs. 1, 2 and 3;

Fig. 11 is a detail sectional view taken on line |l--H of Fig. .10;

Fig. 12 is a fragmentary rear elevation of the machine with parts shown in section on line l2-I2 of Fig. 3;

Fig. 13 is a vertical section taken on line iii-i3 of Fig. l as viewed from the left hand side of that figure;

Fig. 14 is a diagram showing a cutter in operation on a gear blank and showing an illustration of backing oil interference;

Fig. 15 is a schematic layout of the mechanical parts of the machine;

Fig. 16 is a diagram of the electrical controls of the machine.

Figs. l7, l8, l9 and 20 are diagrams illustrating the nature of the cutting action performed by a cutter of the character referred to and the duty imposed on the cutting edges thereof;

Figs. 21 and 22 are diagrammatic views of one of the teeth of the cutter showing a qualitative comparison of the duty imposed on the lateral cutting edges and tip edge when the generative or feeding rotation is performed in opposits directions.

Like'reference characters designate the same parts wherever they occur in. all the figures.

Inthese a cutter of the standard gear shaper type is designated, wherever it occurs, by the reference character C; and the work piece, a gear blank, by the letter W. It will be convenient to describe first th duties imposed on the edges of the cutter in explaining the objects and utility of the invention. For this purpose reference is made to Figs. 17-22. These figures show one tooth of the cutter designated t, in a selected few of the many positions it occupies relatively to the work in generating and cutting out a single tooth space. In the tooth t is represented as taking. the first cut on a blank, the location and form of the tooth space to be eventually finished being indicated by the dotted outline s. The broken lin arcs p and p70 represent the pitch circles of cutter and work respectively, and the line RR. represents theradius of the Work piece through the cent 1' of the respective tooth space. It is assui ed that the cutter and work rotate in th direction of the arrows applied adjacent to their respective tooth pitch circles. The shaded area it indicates in a qualitative way the out made on the first cutting stroke.

Fig. 18 shows the relative positions of the cutter tooth and work piece after they have rotated through a considerable angle about their respective. centers. For convenience of comparison, these figures and those following show the work piece in the same position and repr sent the cutter tooth as though the cutter had been rolled in a planetary manner around the axis of the work. Actually both rotate about their respective axes without change of position (except for cutting reciprocation and backing oil) but the cutting action and penetration of the cutter teeth into the work would be the same if either were revolved around the other. Here the shaded area (1 represents the depth of the out being taken when the cutter is in the position shown, the dotted boundary of that area representing the position of the cutter tooth when making the preceding out. Fig. '19 shows the relative positions of cutter tooth and Work at a somewhat later stage, and here the shaded area 41 represents the depth of the out being taken. Fig. 20 shows the condition at a considerably later stage, when the cutter tooth has passed slightly beyond the line of centers and has nearly completed the generation of the space in the work 4 piece. When in this position the leading edge is cutting a chip represented by the area a in the corner of the tooth space and the trailing edge is cutting a chip represented by the shaded area a at and near the mouth of the space, the portion of that edge at and near the tip having previously completed the inner corner and fillet s.

Fig. 21 indicates by the shaded areas adjacent to the side edges and tip of the tooth, the integration of all the cuts made in the course of gen-- erating any tooth space. It will be noted that the depth of the shaded area adjacent to the leading edge e of the tooth is greater than that of the area adjacent to th trailing edge e. Actually the depths of individual cuts are much less than as indicated in these diagrams, for a cutter may take great many strokes, in the order of scores or hundreds, in generating a single space in the work. But comparatively, these depth dimensions show that a greater amount of cutting is done by the leading edge than by the trailing edge. The facts thus indicated are supported experience, and it has been found necessary to sharpen cutters before the trailing edges of the teeth have become dull.

When the rotation of the cutter and work is reversed, the edge e of each tooth becomes the leading edge and sustains the greater amount of wear. This condition is shown in Fig. wherein the arrow ows that the cutter has been rotated clockwise, whereas the rotation wascountor-clockwise in the operations represented in Figs. l'Z-Zi. In Figs. 21. and 22 the arc to designates the base circle of the cutter tooth curves the line la is the line of action when rotating counter-clockwise and Za is the line of action in the clockwise direction.

The invention includes both the method of reversing the direction of rotation at suitable intervals in the courseof generating anumber of gears and means combined with other features of a gear shaping machine by which such reversals are effected. It also includes means whereby the direction of backing 01f of the work from the cutter, or vice versa, may be adjusted and automatically shifted to one side or the other of the line of centers when the directions of rotation are reversed. The conditions under which such changes or direction are required are illus trated by 14. (Sheet 1) The cutter C in Fig. 14 is represented as rotating clockwise and as operating on a partially cut gear blank W. The form and pitch of the cutter teeth are such that interference with the adjacent uncut. part d of the blank would occur if the blank were backed off on the line of centers D-D. To avoidinterference then, the backing off is performed ina direction inclined to the line of centers, such as that indicated by the line g. Conversely, when the rotation of the cutter is,counterclockwise, there would be a corresponding interference at the opposite side of the line of centers, and then the backing 0d must be in a direction such as that indicated by the line it, the inclination of which with the line of centers is opposite to that of the line 9'.

I will now describe the salient features of an organized gear shaping machine provided with means for efiecting the reversals previously do I scribed.

The cutter C is secured to the lower endxoi a cutter spindle i6 (Fig. 1) which is reoiprocable endwise, and rotatable in a cutter saddle-or carriage Hwhich is supported-to travel on guide ways 12, iii on the supporting structure 13 of the;

machine. Reciprocation is imparted to the spindle by a. lever I4, mounted on a bearing surrounding and coaxial with a shaft 1 5, and having a gear segment on one arm which meshes with enveloping rack teeth It on the spindle. The other arm of lever i4 is coupled by an adjustable connecting rod H with a crank pin [8 carried by and radially adjustable on a disk E9 on the forward end of a crank shaft 25 (Figs. 4 and 13). On the rear end of shaft 20 are mounted fast and loose pulleys 2i and 22 adapted to be driven by a belt from an electric motor, a counter shaft, or other suitable source of power. Such a motor may be mounted on any part of the machine, or elsewhere, suitably for driving a belt that can run interchangeably on each of the pulleys 2i and 22. It is not shown in these drawings except in the electrical diagram, Fig. 16, where it is designated by the numeral 23. For the purpose of this description it may be called the main motor.

Rotation is imparted to the cutter spindle It! by a coaxial worm gear 24 rotatably mounted in bearings in an elevated part of the saddle l I and with which the spindle has engagement by means of guides in the nature of splines, a part of which is shown at 25 in Fig. 1. The worm gear 24 is driven by a worm 26 (Figs, '7 and 15) keyed to a shaft 21.

The work piece W is mounted on a work spindle 28, which is rotatably mounted in a quill 29 held by an apron 3!] and supported on the machine base. A worm gear 3| is secured to the work spindle and is driven by a worm 32.

The guideways l2 lpermit movement of the cutter saddle l 1 toward and away from the work spindle. Advance of the saddle for feeding the cutter to the correct depth and retraction to permit changing of the work pieces are effected by a depth feed cam 33 on a shaft 34, and a weight 35 (Figs. 3 and 4), which are operatively associated with the cutter saddle in a manner later described.

A comprehensive view of the driving connections whereby the spindles and depth feed cam are rotated, is given by the schematic layout in Fig. 15. An electric motor 35, which may be called the feed motor, drives a shaft 31 by means of a coupling 38. Shaft 31 carries a gear 39 which, through'mating gear 45, shaft 4! and gear pair 42 drives the worm shaft 21 by which the cutter spindle rotating gear 24 is rotated. Shaft 31 also drives, through a set of changeable gears 43, a shaft 44 on which is mounted a bevel gear 45. A depending shaft 45 carries on its upper end a gear 41 in mesh with gear 45 and on its lower end a bevel gear 48 which is adapted to mate with either of two bevel gears 49 and 50 on the shaft 5| on which the worm 32 is splined for rotating the worm gear 3| of the work spindle. The depth feed cam 33 is driven from shaft 44 through a clutch 52, a shaft 53 to which this clutch is splined, a gear 54 on shaft 53, a gear 55 meshing therewith on a shaft 56, a worm 51 on shaft 56 and worm gear 58 on shaft 34 of the cam.

It is necessary that the depth feed cam rotate always in the same direction. Hence, when the rotation of the cutter and work spindles is reversed, by reversal of the feed motor 36, the drive for the cam must be reversed relative thereto; and for reversing it a. bevel gear 59 is mounted free on the shaft 53 and is held in mesh with the bevel gear 41. Being at the opposite side of the axis of gear 41 from gear 45, gear 59 rotates op- 6 positely to the shaft 44. shiftable endwise on shaft 53 and has clutch teeth on opposite ends capable of being brought into mesh exclusively either with complemental teeth on the end of shaft 44 or teeth on the adjacent face of gear 59. The details of this reversing clutch and gearing are shown in Fig. 9.

Fig. 15 shows also a belt shipper 55 connected with an operating rod BI and operable thereby to shift the driving belt from either of the tight and loose pulleys 2i and 22 to the other. per 65 carries an adjustable switch actuator 52 in position to operate an electric switch 63; and the depth feed cam shaft 34 carries also a switch cam 54 for controlling an electric switch 65. These switches form part of starting, stopping and reversing means for the feed motor 35 and another motor later described. C'am 54 is constructed to cause closing of switch 55 during only a small fraction of its rotation, and near the end of its rotation.

The depth feed cam acts on the cutter saddle through a roller 65 (Fig. 8) carried by a rack 6'! supported to slide on a part of the guideways [2 and with which the saddle is coupled through a pinion 65 in mesh with the rack and forming an operative part of shaft i5; said shaft being contained rotatably in a sleeve 65 (Fig. 3) mounted in the saddle II and on which lever l4 has its bearing. Shaft I5 is normally locked against rotation relative to the saddle and may be manually turned to adjust the position of the saddle and cutter spindle to greater or less distances from the cam. The weight 35 is suspended by a chain it which overlies and hangs from a sprocket H on a shaft 12 (Fig. 3). Shaft 12 carries a pinion 13 in mesh with a rack I4, which is so connected or engaged with the cutter saddle that the force exerted by the weight holds the cam roll 66 against the depth feed cam and retracts the saddle whenever the cam permits. The parts last described are substantially like corresponding parts shown in the patent of the United States to Fellows No. 1,463,806, dated August 7, 1923, except that a worm carried by an upright shaft '15 and an external gear 76 meshing therewith, keyed to shaft l5, for adjusting the pinion 68, are substituted for the spur pinion and internal gear couple for that purpose shown in said patent.

The depth feed cam has a recess 71 which permits retraction of the cutter from the work, a rise 18 which advances the cutter to the work and feeds it to depth, and a dwell occupying the major part of its circumference, which holds the saddle in place until a series of teeth have been cut.

The shipper rod 5| projects from the front of the machine and carries a handle '35 whereby it may be pulled forward to shift the belt from the loose to the fast pulley. A spring 8!] sur-- rounding the rod and reacting between the shipper and an abutment on the machine frame tends to move the shipper backward to place the belt on the loose pulley. A latch lever 8! is pivoted to the machine frame at 82 and carries a latching tongue 83 (Fig. 8) adapted to enter a notch in the side of the shipper rod when the latter is in its forward position. Lever 81 has an arm 84 extending toward the depth feed cam and having a contact surface 85 adjacent to the orbit in which a trip stud 85 on the depth feed travels. When the latch lever is engaged with the shipper rod, the contactsurface 85 extends across the path of stud 86. far enough so Clutch 52 is a sleeve The shipthat the stud, in wiping across it, causes the latching tongue to be Withdrawn from the shipper rod. The latch lever is so arranged that gravity causes its latching tongue to rest on the upper side of the shipper rod and to enter the notch therein when the rod is drawn forward.

The control equipment of this machine for the motor 38, and another motor later described, is set into action by the switch '68 every time the shipper rod Si is pulled forward, and the con trols include means for reversing the motors with each actuation. The machine is stopped when the depth feed cam completes a rotation and is organized so that the series of teeth of the work gear is completed within that length of time. Means are provided under control of the beltshipper rod for reversing the drive for the depthfeed cam every time the shipper is moved to start the machine, so that the cam will rotate at all times in one and the same direction. Suchrneans comprise a pinion 83 mounted to rotate one: fixed pivot pin. 89 (Figs. 4, and 6) in mesh with a series of rack teeth so cut in the upper side of the shipper rod til. An arm 91 connected with this pinion carries a pawl $12 cooperating with a ratchet 93 beside and coaxial with pinion 88.. The ratchet has two notches at diametrically'opposite points arranged to receive the toe of the pawl and shaped so that the .pawl will rotate the ratchet when the shipper rod is pulled iorward, and travel free when the rod is retracted. The pinion is designed to be turned through somewhat more than a half revolution, but less than a whole turn, with each movement of, the

belt shipper. A cam il l rigidly coupled. with the ratchet 93 has a high pointat one side of its axis, a low point at the other side, and eccentric intermediate portions; It engages a roclilS which is sliclable in guides sit and .Ql',:and is held in contact with the cam. by a spring as (see Fig. 7). Rod 55 is engaged by a fork. on 'a lever arm 95? which is pivoted at. iiill. and has a forked. arm Hilembracing the clutch sleeve 52 in coupled engagement with a ring Hi2 which is embraced by'fianges. onthe clutchsieeve, as shown-by 9.. i hus the clutch. sleeve is coupled. with the gear in! after every alternate forwar dmovement of the shipper rod, andwithrthe shaft id after eachv intermediate iorward movement, and re-- mains in such coupled engagementeach' time while the depth. iced cam rotates all the way around since the high andlow points-oi the cam are. suitably shaped and arranged for that purpcsea'nd the cam remains stationarywhen the shipper rod is retracted.

For backing off :the work spindle to preventdraw the apron and quilliroin a seat it"? in the machine base- (Fig. 1), against which it is held: while cutting strokes are made.v A system of levers and push rods is interposed-between the lever Hi l and acam mil-(Fig. l3) oaths-crank shaft 2!]; such-system consisting of a plunger Hi9 having a. roller llli'in' contact with 13.116.38.111, a rod H I engaged by the plunger and-bearing on an adjustable abutment in one arm,.-i 2,. of a bell crank lever (Fig; 12 pivoted at Hz, the arm lie of whichohears cn one end of a rod H5, whose other end bears on the lever H14.

Spring Hill exerts force holding all of these partsin engagement and eliminating backlash, and the adjustable abutment in arm I 12 enables the cam, acting through this transmission system, to hold the quill is firmly against the seat till. The cam has a low dwell and a high dwell, each subtending nearly half its circumference and so disposed that the high dwell causes the spindle quill to bear on seat ml throughout the whole of each cutting stroke, and the low dwell permits the spring Hi6 to back ofi the work spindle at the beginning of each return stroke and hold it clear of the cutter throughout the course of the return strokes.

The work spindle is guided in its backing off and return movements by guide block Hi5 (Fig. 4) having a contact surfaceadiacent to the sp die against which bears a sliding shoe H1 which is seated in a recess H3 in a flange its on the quill 29. The guide block H5 is carried by the upper end of a shaft in which has a rotative bearing in the machine base, so that the block can be inclined at various angles with respect to the line of centers or the cutter work spindles.

that the plane in which the axes of these spindles lie. The outer surface of the shoe ii! is cylindrical and coaxial with the shaft 52% when the work spindle is at one location between the limits of its backing off movement; and, as this movement is very short, the said curved face is substantially co trial with the shaft in all positions of the spindle. .As the recess H8 is complemental to the curved face of the shoe, the latter has a floating engagement with the quill which enables it to adapt itself to all inclinations of the guide block H5. Abutment screws I22 and 923 are mounted in a fixed part of the frame to be engagealole with the block 1 ill at points on opposite sides of the pivotal axis thereof, whereby to adjust the inclination of the block, with or without permittingcscillative movement of the block, and to limit the range of such osciliative movement when permitted. When the abutment screws are in the position shown in Fig. 4, an oscillative movement of the block M5 to equal and opposite angles with the line of centers is permitted.

Automatic angular shifting of'theguide block '5 forthe purposes explained in connection with the foregoing description of Fig. 14 is accomplished herein by an electric torque motor 25 having a shaft 25, on which is mounted a Worm 126 meshing with teeth on the adjacent end of the guide block. This torque motor typifies any means capable of rotating in opposite directions and of exerting constant force on a driven part when such part is blocked. It is correlated with reversing means controlled by the switch 6.3 so as to be impelled in reversed directions every time the feed motor is reversed and set in action.

This machine is operable for cutting either external or inte nal gears and forthat' purpose the shaft 5'} which drives the worm 32 for rotating theworlzspindle is shiftable endwise to put either gear G9 or Bil in mesh with the gear 58' on shaft l8. When gear id is in mesh, as shown in Figs. 2 and 3', the work spindl'erotates oppositely to the cutter spindle, and when gear is in mesh it rotates in the same direction as the cutter spindle in all reversals. Shaft 5! has a splined engagement with worm 32 and is seated at one end ina bearing block F27, being restrained against endwise'movement relative to the'bea-ring block? by the gear 5!! and-a nut on the rear end of: the shaft, between which the block is. confined,v

The bearing block can be moved endwise in the housing I28 and is secured by a screw I29 (the extremity of which enters alternatively either of two sockets in the block), in the positions for meshing the gears 49 and 56 respectively with gear 48 (see Fig. 3).

Housing I28 is swiveled on shaft 46 and a pivot I30 alined with the shaft so that the worm 32 can be shifted out of mesh with worm wheel 3i and adjusted into correct mesh with the wheel. Its outer end rests on an adjustable abutment I3I (Figs. 3 and 11) and it carries a nut I32 at one side into which a screw I33 enters. The head of the screw and a washer I36 bear on the opposite ends of a tube I35, through which the shank of the screw passes, and this tube passes through a stud I36 in screw threaded engagement therewith, whereby it may be adjusted in the directions necessary to move the worm toward and away from the worm wheel.

The mode of operating the machine will be understood from the foregoing description with reference to the electrical diagram (Fig. 16).

The diagram shows a push button starting switch I37 and a starter I38 for the main motor 23 having an actuating coil I38a, including switch contacts by which the motor is connected with the power lines when the coil is energized, and anadditional contact I39 for interlocking. There is a normally closed push button stop switch in the circuit of coil I38a.

A starter MI for the feed motor 36 includes two sets of switch contacts, one of which is arranged for connectingthe motor with the power lines for forward running, by an electromagnetic coil I 4IF when the latter is energized, and the other for connecting the motor to run reversely, by a coil MIR when that coil is energized and coil I IIF is deenergized. The forward. switch includes a contact I Ma for interlocking, which is shifted from open to closed position when the forward switch is closed; and the reversing switch includes a contact I IIb for interlocking, which is put in circuit closing position when the reversing switch is closed.

A starter I42 for the torque motor I24 includes forward and reversing switches similar to those of the starter MI, of which the forward starting closed and the other three are open (as shown) when coil I43 in deenergized. When coil I63 is energized, these contacts are all put into the opposite condition or phase.

Another set of contacts 2a, 2b, 2c and 2d are connected for simultaneous operation by an electromagnetic coil havin two parts designated I44 and Ma. The contacts 211 and 2b are closed, and contacts 20 and 2d are open when the coil is deenergized. When the part Mia of this coil is energized, contacts 2a and 2b are opened and contacts 20 and 2d are closed; and they remain so, due to permanent magnetism of the magnet armature and the frame iron of the switch struc ture, when the current supply to that part of the coil is broken. Coil parts I 44 and I did are so connected that when current is applied through both parts of the coil, that magnetic effect is overcome and the contacts return by gravity to the positions shown in the diagram. A commercial switching apparatus known as a mechanically-held relay, having the characteristics To here described, is used as this part of the equipment.

The switches 63 and 64, previously described, are shown on the diagram in their relation to th other parts.

To start the machine from inactive condition, the push button switch I31 is momentarily closed (stop switch I46 being normally closed.) Coil I38a is then energized and closes the switch contacts of starter I38 to set the main motor 23 in operation. It also closes the contact I39 to establish a shunt circuit around the switch I31 so that the coil will continue operative after the push button has been released. Thereafter, the following steps of operation occur in the course of cutting two gears in succession.

1. The shipper rod 6| is pulled forward to shift the driving belt from the loose pulley 22 to the fast pulley 2|, causing the crank shaft 26 to rotate, and at the same time closing switch 63. Current then fiows through the closed contacts ia and 2a to the coil I4 IF, whereby the feed motor 36 is started to cause the work and cutter to re volve in what may be called, for the purposes of this description, their forward directions of rotation by closing of the switch contacts previously referred to as the forward contacts of starter I 4 I. At the same time the contact I 4 Ia is closed, which establishes a shunt circuit around the contact Ia. The coil I421 is in circuit connection with switch contact 2a, and is then energized to actuate one Of the sets of contacts of starter I42 and put the torque motor I24 into action for placing the back-off block II6 into correct position corresponding to the direction of rotation of the cutter and work.

2. When the work piece is finished, the depth feed cam 33 and control cam 64 have nearly completed a revolution and cam 64 has reached the position in which it briefly closes the contacts of switch 65 before the machine stops. Closing of switch 65 causes coil I43 to be energized and all the contacts which it controls to be shifted .to the opposite positions from those shown in the diagram. Contact I b is closed, establishing a shunt circuit around switch 65 through coil I 43, whereby the coil remains energized after switch 65 has opened. Closing of contact Id at the same time provides a current path through the previously closed contacts Ia and 2b to the coil part I 44, whereby contact 2a is shifted to open the circuits of the coils IMF and IMF. This stops the feed motor 36 and removes power from the torque motor 624. At the same time contact 21) is opened and contacts 20 and 2d are closed. Although contact 2b is then open, all thes contacts remain magnetically latched by the permanent magnetism of the structure in the positions to which they were shifted when coil part I 44 was energized.

3. The final part of the rotation of cam 64 releases switch 65, whereby the latter automatically opens.

4. At the end of the rotation of the depth feed cam, its trip stud operates latch lever 8| to release the shipper rod 6I, whereby the contact 63 is opened, and all moving parts of the machine except the main motor 23 come to rest, and the coil N33 is deenergized, causing the contacts Ia, Id to return to the positions shown in the diagram. The contacts 2a-2d, however, remain in the positions opposite to those shown.

5. For cutting the next gear, with rotation of the cutter and work in the opposite direction, the shipper rod is again pulled forward and switch E3 closed. Current then flows through the closed contacts Id, 20 and the reversing coils MIR and MZR. Coil IMR closes the reversing switch contacts of the feed motor starter Hll, whereby the cutter and work are rotated in the reverse direction, and contact ldil) is closed. Coil l 'iER closes the reversing switch contacts of the torque motor starter M2 and causes the torque motor 24 to shift the guide block H8 to the opposite inclination.

6. The machine continues in operation until the gear then on the work spindl is completed and switch '5 is again closed by cam E i. At this time the coil M3 is energized and shifts contacts let-4d to the opposite positions from those shown in the diagram, as first described. Current flows through the now closed contacts hill), is and 2d to energize the entire coil 1M and Mac, whereby the contacts 2o-2d return to the positions shown in the diagram, and the coils MIR and MZR, are deenergized so that the contacts of starters MI and H52 are opened, and power is removed from the feed motor 36 and torque motor lit.

7. The depth feed cam 33 and switch cam il kick forward to open the switch S5.

8. The shipper rod is shifted to stop the rotation of crank shaft 26 and open switch 63.

Further operations of the shipper rod cause the actions herein described to be repeated; alternate operations causing the feed and torque motors to be driven in the so called forward direction, and the intermediate operations causing these motors to be driven in the so called reverse direction.

It is to be understood that many variations from the specific machine and parts thereof may be made without departing from the spirit and scope of the invention, and all such variations within the broad ambit of the principles embodied herein are embraced within the scope of the protection claimed.

What I claim as my original and novel inven tion is:

1. A gear generating machine including a gear shaped planing cutter having cutting edges at one end, a rotatable cutter spindle on which said cutter is mounted, a rotatable work spindle adapted to carry a gear blank, one of said spindles being movable endwise reciprocably, mechanism for so reciprocating the endwise movable spindle, reversible driving means coupled with the spindles organized to rotate them simultaneously, control means for starting and stopping the action of said driving means, and means controlled by said control means for reversing the driving means whenever said control means is operated to start the driving means.

2. A gear generating machine comprising a cutter spindle and a work spindle, one of which is reciprocable endwise, a gear shaped planing outter having teeth with cutting edges on one end. secured to the cutter spindle, one of the spindles being movable toward and away from the other for alternately efiecting a backing off movement between a work piece and the cutter and bringing them into cutting relation, a guide arranged for controlling the direction of backing oil and return movements, adapted to be set at difierent inclinations to a plane including the cutter spindle axis and the pitch point of the cutter with a work piece on the work spindle, reversible driving means for rotating said spindles simultaneously in harmony, means for shifting said guide, and control means for starting said driving means, said control means including means for ill reversing the driving means and causing the guide shifting means to be actuated whenever said driving means is put into action.

3. In a gear generating machine of the shaper type having cutter and wori: spindles and a gear shaped planing cutter carried by the cutter spindle, a reversible motor in driving connection with both spindles for rotating them when set into operation, a controller operable to start said motor and means operated by said controller for causing the directions of rotation imparted by the motor to the spindle to be reversed.

i. A gear generating machine comprising a supporting structure, cutter and work spindles mounted rotatably and one of them being re ciprocable endwise, a gear shaped cutter having cutting edges at one end of its teeth secured to the cutter spindle. means for reciprocating one of said spindles, means for moving one of said spindles away from and toward the other in time with reciprocations of the reciprocable spindle to bring the cutter and a work piece in cutting relation when cutting strokes are made and into a backed off relation for return strokes. a guide disposed to control the direction of such backing oil movement and being angularly adjustable to alter such direction, reversible driving means for rotating said spindles simultaneously, reversible guide actuating means connected with said guide to shift the position of the guide angularly when actuated in opposite directions, and means for causing simultaneous reversals of said drivin means and guide actuating means.

5. A gear generating machine comprising a supporting structure, cutter and work spindles mounted rotatably and one of them being reciprocable endwise, a gear shaped cutter having cutting edges at one end of its teeth secured to the cutter spindle, means for reciprocating one of said spindles, for moving one of said spindles away from and toward the other in time with reciprocations of the reciprocable spindie to bring the cutter and a work piece in cutting relation when cutting strokes are made and into a backed off rel ion for return stroke ,a carriage on which the other spindle is mounted movable to effect separation and approach between the spindles for depth feeding, a depth feed cam formed and disposed to control movement of said carriage, a reversible driving means for rotating the spindles simultaneously, reversible transmission connections between said driving means and the depth feed cam for propelling the latter, a controller for reversing said driving means, and means actuable by said controller for reversing the action of said cam propelling connections at the same time.

6. A gear generating machine comprising a supporting structure, cutter and work spindles mounted rotatably and one of them being reciprocable endwise, a gear shaped cutter having cutting edges at one end of its teeth secured to the cutter spindle, means for reciprocating one of said spindles, means for moving one of said spindles away from and toward the other in time with reciprocations of the reciprocable spindle to bring the cutter and a work piece in cutting relation when cutting strokes are made and into a backed oil relation for return strokes, a carriage on which the other spindle is mountedmovable to effect separation and approach between the spindles for depth feeding, a depth feed cam formed and disposed to control movements of said carriage, a reversible driving means for rotating the spindles simultaneously, reversible transmission connections between said driving means and the depth feed cam for propelling the latter, a controller for reversing said driving means, means actuable by said controller for reversing the action of said cam operating means at the same time, a guide arranged to control the direction of backing oil movement between the spindles and being shiftable to alter such direction, reversible impelling means coupled with the guide for angularly moving the latter in one direction or the opposite direction when reversed, and means controlled by said actuatorfor reversing said impelling means when the driving means is reversed.

7. A gear shaping machine comprising a supporting structure, a cutter spindle and work spindle mounted rotatably on said supporting structure and one of said spindles being reciprocable endwise, a gear shaped planing cutter having cutting edges on one end of its teeth mount- 8. A gear shaping machine comprising a supporting structure, a cutter spindle and a work spindle mounted rotatably on said supporting structure and one of said spindles being reciprocable endwise, a gear shaped planing cutter having cutting edges on one end of its teeth mounted on the cutter spindle adapted to cut tooth spaces in a Work piece mounted on the work spindle, motive means in driving connection with said reciprocable spindle for imparting reciprocating movements thereto, a controller operable to start and stop the reciprocating movement of said spindle, a reversible motor in geared connection with both spindles for rotating them simultaneously, a carriage on which one of the spindles is mounted movable to alter the distance between the spindles for depth feeding and to permit changing of work pieces on the work spindle, a depth feed cam operatively associated with said carriage for controlling the movements thereof, reversible transmission mechanism between said driving means and depth feed cam for rotating the cam, means controlled by said controller for causing the driving means to run in alternately opposite directions with successive operations of the actuator to cause reciprocating movement of the reciprocable spindle, and means operable by the controller at the same times for reversing the transmission mechanism by which the depth feed cam is driven.

9. A gear generating machine comprising a supporting structure, cutter and work spindles mounted rotatably on the supporting structure, one of said spindles being reciprocable endwise, a gear shaped planing cutter secured to the cutter spindle, an apron in which one of the spindles is mounted movable on the supporting structure to impart backing off and return movements to the spindle which it carries relative to the other spindle, a guide located beside the apron in engagement therewith for controlling the direction of such backing on and return movements and being angularly shiftable to vary that direction, adjustable stops associated with said guide to establish limits to its angular movements in opposite directions, a reversible electric torque motor coupled with said guide to shift the latter to one or the other of such limits and hold it in contact with one or the other of said stops when oppositely actuated, an electric driving mtor in driving connection with said spindles for rotating both simultaneously, and control means operable to reverse the action of said torque motor and driving motor simultaneously.

EDWARD W. MILLER.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,862,202 Simmons June 7, 1932 2,266,889 Miller et al Dec. 23, 1941 

